kottmann



March 17, 1936. A, KOTTMANN 2,034,345

CALCULATING MACHINE Filed June 1, 1934 7 Sheets-Sheet l March 17, 1936.

A. KOTTMANN 2,034,345

CALCULATING MACHINE Filed June 1, 1934 7 Sheets-Sheet 2 March 17, 1936. A. KOTTMANN 2,034,345

CALCULATING MACHINE Filed June 1, 1934 7 Sheets-Sheet 3 March 17, 1936. KQTTMANN 2,034,345

CALCULATING MACHINE Filed June 1, 1934 7 Sheets-Sheet 4 March 17, 1936. KOTTMANN 2,034,345

CALCULATING MACHINE Filed June 1, 1934 7 Sheets-Sheet 6 E! [E] @IEEIIEEHE 202 [E March 17, 1936.

A. KOTTMANN 2,034,345

CALCULATING MACHINE Filed June 1, 1934 '7 Sheets-Sheet 7 202a 202 19 100 .97 196 .962: f3 .20. 1937.21. 0 17 u y 212 I 216 211219 18 O 15 .99 217 0 10 X I 950x 221 O O 213 212 I G 9 210 f i .98 210 211 211 w 221 320x220 16 A 251 mfl Patented Mar. 17, 1936 t UNITED STATES I 2,034,345 PATENT OFFICE CALCULATING MACHINE Application June 1, 1934, Serial No. 728,603 In Germany June 6, 1933 9Claims.

This invention relatesto calculating machines and has for its main object to provide a ten key calculating mechanism for such machines which shall be reliable and positive in its operation.

The invention will be described with reference to the accompanying drawings.

Fig. 1 shows the calculating machine according to the invention, the cover plates and accumulator being removed. Fig. 2 is a plan of the pin carriage and item entry devices. Fig. 3 is a view, from below, showing the escapement mechanism for the pin carriage. Fig. 4 is a side elevation of the members for actuating the escapement mechanism. Fig. 5 shows the actuating device for the return stroke of the carriage. Fig. 6 is a longitudinal section through the entire machine, with the parts in the initial position. Fig. 7 shows the arrangement of an actuating rack. Fig. 8 is a view corresponding to Fig. 6 and shows the position of the parts when the operating handle is drawn forward, shortly before the printing of a calculated value. Fig. 9 shows the change in position of the parts of the printing mechanism after the impression. Fig. 10 represents details of the printing mechanism. Fig. 11 .is a side elevation of the drive for the control of the accumulator. Fig. 12 shows the accumulator, with its control members in position after being coupled, to the actuating members. Fig. 13 is a side elevation showing the parts in their position for addition. I Fig. 14 is the front elevation of a detail of a control member. Fig. 15 is a side elevation of the accumulator with the tens-carrying means in their initial or neutral position, in conjunction with the main parts of an accumulator drive designed as a rack drive. Fig. 16 is a plan of the arrangements according to Fig. 15, the accumulator being shown on the right half of the figure, and the racks of the accumulator drive on the left, certain plates, which would otherwise conceal the interior of the machine, being cut away. Fig. 17 shows the tens carrying mechanism as operating during subtraction. Fig. 18 shows the plan of the parts required for carrying over the tens, and for the minus setting of the accumulator. Fig. 19 is a side elevation of a part of the machine showing the position of certain parts required in subtraction. Figs. 20 and 21 are two views of the minus key with certain parts co-operating therewith. Fig. 22 shows the locking members. allmated to the minus key, in the locking position. Fig. 23 is an elevation of the drive for the tens carrying shaft. Figs. 24 and 25 are two views, partly cut away, of the actuating members seated on the tens carrying shaft.

The numerical values to be introduced into the machine are introduced in known manner, by means of the keys I (Figs. 1 and 6,), key levers la and intermediate levers 2, into the setting pins 3 of the carriage 4. The setting pins thus raised serve as stops for racks forming the setting members 3|, which are mounted in guide notches of the carriage 4, and, in being set, actuate at the same time indicating wheels 33 which 5 are also mounted on said carriage. The num-'- ber of setting members 3| is the same as that of the rows of setting pins 3. When any of the keys is struck, the corresponding key lever |a depresses a lever I0 (Figs. 6 and 8) which by 10 means of a lug 35 releases a pawl 34 engaging the corresponding setting member 3|. Said member 3|, which was previously retained in the neutral position by the pawl 34, is then free to be actuated by a spring 32 (Fig. 2) and moves towards 15 the left (Figs. 6 and 8) until its end bears against a simultaneously raised setting pin 3, thus setting the member 3|.

By means of an escapement mechanism 6, 1, 8 (Fig. 3) which acts on a rack 9 on the carriage 4 and is mounted on a plate 95 of the machine frame, the carriage 4 is allowed to escape to the left (Figs. 1, 2) to an extent corresponding to the spacing of two adjacent rows of setting pins by the action of a spring M (Fig. 2) each time a 25 key is struck, so that the rows of setting pins pass in succession over the ends of the intermediate levers 2 and the pawls 34 pass in succession over the lug 35 on the lever Ill.

The ratchet mechanism is actuated by the lever I I] (Fig. 6) arranged below the key levers la (Fig. 6). When any of the keys I is struck, the corresponding key lever la depresses the lever III, which in turn depresses the arm I la of a lever I (Fig. 4) and thus'turns the lever about the pivot MD. A presser bar |3 which in turn rocks a pawl 8 is articulated at |2 to the lever H. The pawl 8 actuates the two ratchet pawls 6, I in the desired manner.

The carriage 4 is returned to its original posi 40 tion, when, to effect an addition or a subtraction, the handle i5 is rocked forwardly and backward ly. The movement of the handle I5 is transmitted, by intermediate members |6, l1, l8 (Figs.

1 and 13), a shaft a, a one-armed lever I9 45 (Figs. 1 and 5), and a thrust bar 20, to a thrust pawl 23. The bar 20 has an arm 20a (Fig. 5) by which it is guided in a member 2| mounted in the base of the machine. The thrust pawl 23 is pivoted on a pin 22 and bears, under the action of a spring 24, against a stop 25 on the thrust bar. As long as the handle I5 is in normal position, the thrust pawl 23 is held in the position shown in dotted lines in Fig. 5 because the arm 23a of the pawl 23 bears against a pin 23b on the machine frame. When the handle is moved forwardly the bar 20 is moved to the right (Fig. 5) whereby the arm 23a of the pawl 23 is raised by the pin 23b passing into the position shown in full lines in Fig. 5. When the handle II is returned to normal position and the bar 20 with pawl 23 moves to the left in Fig. 5, the pawl encounters an'arm 26a on a driver lever 26 (Figs. 1, 2, 5) pivoting on a pin 21 and having an arm with a forked end 26b engaging a pin 28 on the carriage 4. The rocking movement of the lever 26 forces the carriage 4 back into the original position (Fig. 1), whilst, at the same time, the pins 3, set at the beginning of the operation, are forced back into their original position, sliding under a member 29 provided with a bevel. Short ly before the handle l5 returns to its initial position the arm 23a of the pawl 23 again encounters the pin 23b on the machine frame, whereby the pawl is restored to the position shown in dotted lines in Fig. 5. If a new number is now set up in the carriage 4 and the latter moves from its normal position, the arm 26a of the lever 26 can move freely over the pawl 23. The return of the setting members 3| will be described later.

Driving or transmission racks 31 (Figs. 1, 6, 7, 8, and 15) on which are riveted secondary racks 38, are provided in the same number and displaceable in the same direction and to the same extent as the setting members 3| in a frame 36 (Fig. 1) mounted in the frame of the machine. Secured on the transmission racks 31 are coupling members 40 (Figs. 1, 6, '1, 8) which are adapted to turn on pivot pins 39, and are swung by springs 4| (Fig. 7) in the direction of a member 42 (Figs. 6 and 8) on a frame 43 carrying an accumulator said frame being disposed above the racks 31 and pivotally mounted on a shaft 44. The accumulator |0| can be raised and lowered by turning the accumulator frame about the shaft 44 and thus brought into or out of engagement with the racks 38 by means of the intermediate pinions 89. The accumulator |0| is raised and lowered by means of a curved member 46 (Figs. 11 and 12) mounted on a shaft 45 which is actuated through intermediate members 92, 93, 94 (Fig. 1) by a shaft 45a, which also effects the return movement of the carriage 4 and is actuated'in turn by the handle l5. Fig. 11 shows the member 46 in its normal position. When the forward movement of the handle l5 and of the curved member 46 begins, a forward wedge-shaped projection 46a on the latter engages a guide roller 41 (Fig. 11). When the movement of the member 46 is continued the roller 41 is forced downwards to such an extent as to allow the under side 46b of the curved member 46 to move over the roller 41. The roller 41 is fixed to a lever 48, pivotable for a distance determined by a pin and slot guide 4811 about a pin 43a on the accumulator frame 43. The lever 48 causes the accumulator |0| to descend as the movement of the curved member continues, and to engage, through the intermediate pinions 89, with the rack 38. The member 42 mounted on the accumulator frame and descending with the accumulator simultaneously brings angular projections or stops 40a of the coupling members 40 into engagement with the teeth of the setting members or control racks 3| (Rig. 8).

Together with the curved member 46 a positive movement is imparted to a riveted hook 50 (Figs. 11, 12) which engages behind a pin 5| provided on the accumulator frame and thus retains the accumulator in the coupled position (Fig. 12)

At the same moment that the locking hook 50 engages behind the pin 5|, the under side 46b of the curved member 46 has passed out of contact with the guide roller 41 of the lever 48. The roller 41 and lever 48 are forced up (Fig. 12)

at the same moment by a lever 53 attached to the curved member 46 and under the tension of a spring 52, so that during the return of the handle into its original position, the guide roller 41 runs back over the upper surface 460 of the curved member. Though the lever 48 is lifted the accumulator is held in its downward position by the hook 50 and the pin 5|. Only when the handle [5 begins its return movement does the hook 50 free the pin 5| whereby the accumulator is returned into neutral position by suitably disposed springs (not shown).

Consequently, during the forward movement of the handle IS, the accumulator is brought into engagement with the racks 38, and is disengaged during the return movement. Similarly during the forward movement of the handle, the actuating racks 31, 38 are coupled with the setting member 3| by the stops 40a of the coupling members 40 actuated by the accumulator frame 43 through the member 42, the coupling being disengaged in the return movement.

When the handle I5 is moved forward, a driver bar (Figs. 1, 2, 6, 8, 11) is advanced the distance corresponding to the numerical value 9 by connecting rods 81, 88 (Figs. 11, 13). By this means all the setting members 3| previously set in accordance with the items to be added, are returned to the zero position. Thereby the actuating racks 31 coupled to the setting members 3| by the coupling members 40 are moved through a distance corresponding to the amount set. Excessive movement is prevented by a limiting bar 90 (Figs. 6 and 8), which is mounted in the carriage 4 transversely in front of the ends of the setting members 3| and stops the latter from being moved beyond the zero position.

As soon as the handle l5 has reached the end of its forward stroke the accumulator |l1| comes out ofengagement with the transmission racks 31, 38 as already described and the setting members 3| are uncoupled from the actuating racks, said members and the numerical control rollers 30 being thus again set to zero.

In the return stroke of the handle l5 and driver bar 85 into the original position, the latter encounters hooked projections 31c (Figs. 6, 7, 8) of the racks 31 and pushes the latter back into the original position (Fig. 8). Excessive movement is prevented by a limiting bar 9| (Figs. 6, '7.

8) mounted in the frame 36 transversely across the ends of the racks 31 which prevents them from being moved beyond the original position. Consequently, the movement of the actuating racks 31, 38 is wholly positive no springs being employed therefore.

When the setting members are in the position corresponding to the numerical value 9" the driver 85 is closely engaged between the opposing surfaces of the hooks 31c and setting members 3|. When said members are set for the value 0 the driver can reciprocate between the two surfaces to an extent corresponding to the value 9 without dispiacing' the racks 31 or the members 3|. When the member 3| is set in accordance with the value 3 the driver 85 describes at first, at the beginning of both the forward and return strokes, an idle movement corresponding to the value 6 and thenpushes the setting member 3|, or the driving rack 31 back into the original posit-ion. The driver 85 therefore actuates all the driving racks 31 by the aid of two stops (hook 310 and coupling stop 40a) that are provided thereon which stop 31c and the left-hand end of the setting member 3| lie in the path of the driver, the hook 31c being fixed on the rack 31 and the stop 48:: being engaged with the member 3| when key-set.

The member 85 and the setting members 3I may thus be regarded as constant stroke and variable stroke reciprocatory members respectively, of drive transmission means for differentially operating the several racks 31 from a single handle I5.

The drawbars 81 and 88 moving with the driver 85 are connected by means of longitudinal slots 81a, 88a (Figs. 11 and 13) with the arm I8 and the curved member 48 of the shafts 45a and 45. Consequently, at the beginning of the forward and return strokes, the handle I describes a certain movement during which the driver 85 is not moved. During this movement, the accumulator MI is brought respectively into and out of engagement and the setting member coupled with or uncoupled from, the driving racks. These operations therefore proceed with the driver 85 at rest.

Intermediate pinions 48 (Figs. 6, 8, 15, 16) are in engagement with the transmission racks 31. The upper portions of the toothed rims of th s-e intermediate pinions 48 are on a level with the gear teeth of the racks 38 riveted on the transmission racks 31. The accumulator MI is laterally displaceable to a slight extent. When it is pushed towards the right, the intermediate pinions 88 of the accumulator engage with the racks 38 and when the accumulator is pushed towards the left, they engage with. the intermediate pinions 48 of the gear driving the accumulator. In the former case, the action is one of addition, and in the latter case one of subtraction.

To provide the lateral displacement of the accumulator IN, the numeral wheels thereof (Figs. 15, 16, 17) are disposed, with the corresponding intermediate pinions 88 and locking pawls I83, in a frame I84, which, in turn, is slidably mounted in a frame 43 adapted to swing on a cross shaft 44. The frame I84 has lateral pins I81 sliding in gaps in the cheeks of the frame 43. At the same time, the numeral wheels of the accumulator I8I are guided into window openings I28 in the cover plate I38.

In changing over to subtraction, the lateral displacement of the frame I84 is effected by depressing a minus key 86 (Figs. 18, 20, 21) provided on the keyboard, said key rocking a lever 88, shaft 88 and lever I88 (Fig. 19) by means of the pin 81 disposed on its stem 85a. The lever I88 produces a lateral displacement of a connecting bar 282, guided in a bracket 281, against the pull of the spring MI. The bar 282 has a bevel 282a which, on the minus key 86 being struck, is pushed under a roller 283 on a lever 284. The displacement of the bar 282 lifts the roller 283 and turns the lever 284 against the action of a spring 284a.

The lever 284 engages in a fork 28% (Fig. 18) of a lever 285, which is pivotaly mounted on pin 288 on the frame 43 of the accumulator, and engages with its other arm 285a, on the one check I84a of the frame I84 that is to be displaced laterally. Consequently, depressing the minus key 85 moves the frame I84 to the right against the spring Hi, the machine being thereby changed over to effect subtraction.

The minus key 86, which is constrained by the spring 288 (Fig. 20) to rise again directly after being depressed is locked in the bottom position, by a locking device, until the subtraction is at an end. With this object, a lever 2I8 (Figs. 18, 20,

21, 22) is articulated to the stem of the minus key, so as to pivot on an axis 2, which lever has an arm 2I2 engaging in a slot 2I3 of a U-shaped holder 2I4.

The holder 2 carries a pawl 2I5, adapted to turn on a pin 2I5, and a locking slide 2I1 guided by a slot 2I1b. Both are drawn together by a spring 2I8. When the minus key is not operated, and the handle is in neutral position, the spring 2I8 draws the pawl 2I5 and the projection 2I1a of the slide 2" towards the lateral faces of the arm 2I2 of the lever 2I8 (Fig. 18). When the minus key 88 is depressed, the arm 2I2 in Figs, 18 and 22 is moved slightly towards the left, whereupon, as shown in Fig. 22, the pawl 2I8 engages behind the arm 2I2 and locks the key 86 in bottom position.

Articulated to the pawl 2I1 at 2I8 is a lever 22I (Fig. 21) which is influenced by a curved cam 228 moved by the handle I5 through the rods I8, I1, I8, I8.

On the handle I5 being operated in performing subtraction, and the curved surface 228 moved with it, the control lever 22I, lying in a notch 228a in said cam is forced out of the notch against the action of the spring 22Ia and now slides over the periphery of the cam. By these means the slide 2" and the pawl 2I6 (Fig. 22) are raised, so that the ascending pawl 216 releases the arm 2I2 of the lever 2I8. Said arm 2 I 2 (Fig. 22) can therefore spring a little towards the right, but in so doing it bears against a projection 2 No on the slide 2 I 1 and is retained thereby until the return of the handle I5 into the original position causes the end of the control lever 22I to re-engage in the notch 228a, under the influence of the spring 22Ia. By this means the slide 2" (Fig. 22) is again slightly depressed into its original position represented in Fig. 18, so that the arm 2I2 of the lever 2I8 is released. I The lever 2I8, the minus key 86, and all the parts displaced by the latter, then return to their original position. In particular, the frame I84 is also returned to its left-hand end position by the springs II8, thus re-setting the machine for addition.

The upper edge of the cover plate I38 containing the window openings I28 (Fig. 16) is provided with guide slots I88, in which levers I I8 for preparing tens-carry-rotatably mounted about an axis I88 (Figs. 15, 16, 1'1) and laterally displaceable within certain limits-are guided in such a manner that, during the change over from addition to subtraction, they share the lateral shifting of the frame I84 and their ends II8a are always within the sphere of movement of tens-carry preparing lugs mm on the numeral wheels I M.

If, during addition or subtraction, one of the numeral wheels I8I of the accumulator passes from 9 to 0, or from 0" to 9. the cam I8Ia on the numeral wheel will turn its allotted preparatory lever II8 causing its rear extremity IIIlb to press on an arm lb of apawl H1 and, aided by the spring I I8, brings said pawl into a position, in which it looks the lever H8 in the preparatory position.

Pins 80 on thelever II8 engage longitudinal slots III in slides II2 which are guided by transverse notches on a shaft I88. The corners II2a (Fig. 17) of slides of those levers II8 that are locked in the preparatory position lie within the sphere of movement of cams I I3, which are oilset on the shaft 44 round which the frame 43 of the accumulator I8I swings, and therefore the shaft 44 is also the driving shaft of the tens carrying mechanism. It is actuated after the values have been transferred into the accumulator and the latter is again brought out of engagement with its actuating mechanism, the shaft 44 making one clockwise revolution for each operation of the machine. The cams H3 then displace, to'

the right, theslide H2 of any lever 'IIO (Figs. 15 and 17) that is locked in the preparatory position.

The drive of the tens-carrying shaft 44 is shown in Figs. 23, 24, and 25. By means of rods I6, l1, I8, I9, 20 the handle I5 actuates a toothed sector 221, which gears with an idle pinion 224 on the shaft 44, and is provided with such a number of teeth that it imparts one revolution to the pinion, in one or the other direction, both during the forward and return movement of the handle. The hub 225 (Fig. 25) of the pinion 224 carries a driver tooth 226 which lies close in front of a disc 228, keyed on the tens carrying shaft 44 and provided with a driver pawl 230 which is under the tension of a spring 229. When the machine is in neutral position, said pawl lies in the position, in relation to the driver tooth, shown in Fig. 25. During the forward movement of the handle I5, the pinion 224 and the driver 226 (Fig. 25) describe one clockwise revolution. The pawl 230, disc 228 and shaft 44 do not share this movement, but the driver tooth 226 describes an independent clockwise revolution at the end of which it slides under the pawl 230, so that the relative position of driver 226 and pawl 230 is again the same as shown in Fig. 25.

During the return stroke of the handle I5, the pinion 224 and driver tooth 226 are turned in the opposite direction and carry along the pawl 230. disc 220 and shaft 44, which latter describes the revolution necessary for actuating the tens carrying slide H2.

Pivotally mounted on pins I24 and I24a on the slides I I2, are two tens carrying pawls H4, H5 (Figs. 15, 17), which coact by means of lever arms H411 and H511 and, when the tens carrying device is out of action, are held by the spring I26 in the position shown in Fig. 15, in which the pawl H4 bears against the pin I25. The tip I I5b of the lower pawl I I5 is bent sideways to the same extent as the frame I04 is displaced laterally during the change over from addition to subtraction. The two pawls H4 and H5 are so arranged that, when the frame I04 is in the left position (referred to Fig. 16), that is to say, set for addition, the intermediate pinions 89 lie in the same vertical plane as the tips H4b of the pawls H4, and when the frame I04 is in the right-hand position, that is, set for subtraction, said pinions 89 are in the same plane as the tips H5b of the pawls H5, and-reckoning from the accumulator order wherein the preparatory cam IOIa has become operative-the pawls H4 and H5 engage in the intermediate pinion 89 of the next higher order of the accumulator.

If, in an order, a carry has been made ready and the slide H2 is pushed towards the right by a cam H3 (Figs. 15 and 17), the pawls H4 and H5 are at first pushed only in a straight line towards the right until the pawl which is operative for the time being has engaged in a tooth gap of the corresponding intermediate pinion 89. After the slide I I2 has been moved a certain distance towards the right, the arm H4a of the pawl H4 strikes against the shaft I09, whereby the arms H411 and H511 of the pawls H4 and H5 are prevented from moving farther to the tion, and the machine is therefore set forhddi tion, the pawl H4 engages in the pinion 89, so that the numeral wheel is turned in the additive direction a distance corresponding to one unit. With the frame I04 in the right-hand position, and the machine therefore set for subtraction, the pawl H5 engages in the intermediate pinion 89 and turns the numeral wheel in the subtracting direction.

Towards the end of the operative movement of the pawls H4 and H5, the arm H5a of the pawl H5 strikes against a pin I21, whereby any over-running movement of the pawls H4 and I I 5, and the numeral wheels they actuate, is reliably prevented.

At the same moment that the arm H5a. of the pawl H5 bears against the stop pin I21, the cam H3 of the shaft 44 slides off the edge H2a of the slide H2. During the further rotation of the shaft 44, a pin H9 on the cam H3 strikes against the downwardly bent end of an arm I I15 01' the locking pawl H1, thus forcing the latter out of the locking position. The preparatory lever IIO then returns to its original position, under the pull of the spring I28, and the slide H2 returns to neutral position under the pull of the spring I20.

The rear ends of the lower edges of the trans-' mission racks 31 are provided with gear teeth 31a (Figs. 6, 7, 8) which are engaged by the toothed quadrants 54, these latter, in turn, carrying on arms 54a type carriers 55 of the printing mechanism. In proportion as the racks 31 are moved by the setting members ill with which they are coupled the type carriers are also raised, in a positive manner. so that, in accordance with the setting of the racks and type carriers, the values transferred into the counting mechanism can be printed on a strip of paper clipped on to a platen 56 (Fig. 8).

The impression mechanism of the printing device (Figs. l, 6, 8, 9, 10) consists of a number of press pawls 51, corresponding to the number of orders in the accumulator, said pawls being' adjacently disposed on a shaft 58 fixed in a frame 60 (Figs. 6, 8, 10) adapted to swing on a shaft 59, parallel with the axis of the platen. The movement of these pawls about the shaft 58 in the direction of the platen is restricted by a bar 6I (Fig. 9), against which the projections 51a of the pawls 51 bear. Pressure levers 63 carrying weights 63a are allotted to the pawls 51, and are controlled by springs 64, but are normally held in a neutral position by locking pawls 65 (Figs. 6 and 8). In addition a locking bar common to all the pressure levers is mounted in the frame of the machine and engages in notches in the levers 53, being released just before the printing operation by devices which will be described later.

The locking pawls 65 form part of the zeroprinting device and coact with releasing pawls I 61, the number of which is the same as that of the transmission racks 31. When the corresponding transmission racks are in neutral position, the tip 61a of each releasing pawl 61 engages in a recess 31b of the transmission rack (Fig. 6).

As soon as the transmission rack leaves its original position, its unrecessed portion passes under the tip of the pawl, thereby turning the pawls 61 and 65 and effecting the release of the pressure lever 63 (Fig. 8). On their right side, the pawls 61 are provided with pins 68, whilst the left sides are provided with lugs 69 of such dimensions that, in each case, the pin 68 of each pawl lies under the lug of the next lower, adjacent pawl, so that if any pawl be raised by its allotted transmission rack all the pawls lying to the right of it in Fig. 1 will also be raised whereas the pawls on the left will remain in the locked position. In printing a value containing a smaller number of figures than there are orders in the printing mechanism, the pawls 65, 61 prevent the impression of s in front of the first numeral of the multi-numeral value to be printed, whereas zeros inside the row of numerals are printed.

During the forward movement of the handle IS, the frame 60, with the press pawls 51, is swung, by means of the shaft 45a, shaft 45, curved member 45, drawbar 13 (Figs. 1 and 11) and the arm 10, towards the platen 56, in such a manner that the press pawls 51 bear against the back of the type carriers 55 and bring the latter so close up to the platen 56 that the type characters almost touch the paper, whereas the pressure levers 63 are held at first in their original position in relation to the frame of the machine by the bar ll. During the swinging of the frame 60, tension is applied to the springs 64 of the pressure levers 53, which springs are attached at one end to the cross bar 6| of the frame 60. Shortly before the handle i reaches the end of its forward stroke, a striker pin (Fig. 13), which is arranged on the lever arm l6, connected to the handle, comes into contact with a surface 16 on a two-armed lever H and deflects the latter in such a manner that its second arm moves a pivotal release member 18 (Figs. 13, 14). The arm 18a of the member 18, which turns on two pivots l9 and 80, moves a pin Ha on the bar II when said member is deflected and swings the bar 1| out of the locking position. A roller 8|, arranged on an angular bend of the same arm 18a influences a rocking member 82 (Fig. 13) so that the latter forces a straight-edge 12 (Figs. 13, 6, 8) intothe toothed sector 54 (Fig. 8). These last described members are relatively arranged so that, in the first place, the straightedge 12 engages in the tooth gaps of the quadrant 54, after which the arm 18a comes in contact with the pin Ha and effects the release of the spring-controlled pressure lever 63. The forward movement of the release member 18 brings a locking pawl 84 (Fig. 13), controlled by a spring 83, into position behind the arm 18b, and locks the release member until the handle is moved back again.

At the moment the locking bar II is being released, the springs 64 swing the pressure levers 53 on the shaft 59 and impart a high velocity to the weights 5311 (Fig. 9). The bent surfaces 52 of the levers 53 then slide downwards on the rear surfaces 51b of the press pawls 51 and, transforming the kinetic energy of the weights 63a and levers 63 into pressure, press the pawls 51 and type carriers 55, slowly but forcibly, against the surface of the paper so that the impression on the paper is produced less by impact than by uniform pressure.

The thrust bar 20, moved by the handle l5 and actuating the return mechanism of, the carriage of the setting members, carries a pin 86 (Fig. 13) which, at the beginning of the return stroke of the handle l5, lifts the curved arm 84:; of the locking pawl 84 and thus frees the locking of the release member 18, by which means the straightedge 12, obeying the pull of a spring 12a (Fig. 8) detaches itself from the teeth of the sector 54, and the locking bar H is released again. During the further return movement of the handle IS, the driver 85 actuated thereby pushes the transmission racks 31 back into the original position, as already described thus returning the type carriers into their original position.

The frame 60 carrying the printing mechanism is also swung back during the return of the handle l5 into its original position'by means of the shaft 45a, shaft 45, curved plate 46 and drawbar 13, the pressure levers 63 being again locked by the descent of the locking pawls 55, whilst, at the same time, the locking bar 1! is enabled by spring tension to engage in the notches in the pressure levers.

The return of the pawls 65 into locking position is rendered possible through the return of the allotted driving racks into neutral position so that the release or control pawls 61 are able to drop into the recesses 31b provided in same, thereby enabling the pawls G5 to move into the locking position.

I claim:

1. A calculating machine comprising an accumulator with numeral wheels, ordinal actuatmg means for the accumulator including reciprocatory racks, a reciprocatory drive member, a carriage traversable relatively to the actuator racks, keys for setting up digit values, digit setting racks in the path of said drive member and movable in said carriage parallel to the actuator racks by amounts determined by said keys, and pairs of stops on said actuating racks, one stop being adjustable with respect to its rack to couple the latter to one of said key set digit setting racks, and the other stop of each pair being fixed on its rack and cooperating with the drive member in restoration of said rack.

2. A calculating machine comprising an accumulator with numeral wheels, ordinal actuating means for the accumulator including reciprocatory racks, a reciprocatory drive member, a carriage traversable relatively to the actuator racks, keys for setting up digit values, digit setting racks in the path of the drive member and movable in said carriage parallel to the actuator racks by amounts determined by said keys and adapted to be restored to initial position by said drive member on its forward stroke, pairs of stops on said actuating racks, one stop of each pair being adjustable relative to its rack to couple the same to a digit setting rack and the other stop of each pair being fixed on its rack and cooperating with the drive member in restoration of said actuating racks on the return stroke of said drive member, and means operative during the forward stroke of the drive member for producing coupling of actuator racks with the setting racks and for uncoupling said racks after their restoration at the end of said stroke.

3. A calculating machine comprising an accumulator with numeral wheels, ordinal actuating means for the actuator including reciprocatory racks, a reciprocatory drive member, means actuated by said drive member for moving the accumulator into and out of engagement with the actuator racks, a carriage traversable relatively to the actuator racks, keys for setting up digit values, digit setting racks in the path of the drive member and movable in said carriage parallel to the actuator racks by amounts determined by said keys and adapted to be restored to initial position by said drive member on its forward stroke,pairs of stops on said actuating racks, one stop'of each pair being adjustable relative to its rack to couple the same to a digit setting rack and the other stop of each pair being fixed on its rack and cooperating with the drive member in restoration of said actuating racks on the return stroke of said drive member, and means on the accumulator operative during the forward stroke of the drive member for producing coupling of actuator racks with the setting racks and for uncoupling said racks after their restoration at the end of said stroke.

4. A calculating machine comprising an accumulator with numeral wheels, ordinal actuating means for the accumulator including reciprocatory racks, a reciprocatory drive member, a carriage traversable relatively to the actuator racks, keys for setting up digit values, digit setting racks, in the path of said drive member and movable in said carriage parallel to the actuator racks by amounts determined by said keys, an indicator in said carriage cooperating with the setting racks, and pairs of stops on said actuating racks, one stop being adjustable with respect to its rack to couple the latter to one of said key set digit setting racks, and the other stop of each pair being fixed on its rack and cooperating with the drive member in restoration of said rack.

5. A calculating machine comprising an accumulator with numeral wheels, ordinal actuating means for the accumulator including reciprocatory racks, a reciprocatory drive member, a carriage traversable relatively to the actuator racks, keys for setting up digit values, digit setting racks in the path of said drive member and movable in said carriage parallel to the actuator racks by amounts determined by said keys and adapted to be restored to initial position by said drive member on its forward stroke, pairs of stops on said actuating racks, one stop of each pair being adjustable relative to its rack to couple the same to a digit setting rack and the other stop of each pair being fixed on its rack and cooperating with the drive member in restoration of said actuating racks on the return stroke of said drive member, means operative during the forward stroke of the drive member for producing coupling of actuator racks with the setting racks and for uncouplingsaid racks after their restoration at the end of said "stroke,'"and' means common to all the setting racks for halting-them in initial position.

6. A calculating machine comprising an accumulator with numeral wheels, ordinal actuating means for the accumulator including reciprocatory racks, a reciprocatory drive member, a carriage traversable relatively to the actuator racks, keys for setting up digit values, digit setting racks in the path of the drive member and movable in said carriage parallel to the actuator racks by amounts determined by said keys and adapted to be restored to initial position by said drive member on its forward stroke, pairs of stops on said actuating racks, one stop of each pair being adjustable relative to its rack to couple the same to a digit setting rack and the other stop of each pair being fixed on its rack and cooperating with the drive member in restoration of said actuating racks on the return stroke of said drive member, meansoperative during the forward stroke of the drive member for producing coupling of actuator racks with the setting racks and for uncoupling said racks after their restoration at the end of said stroke, means common to all the setting racks for halting them in initial position, and means common to all the actuator racks for halting them in initial position when they are restored thereto by the return stroke of the drive member.

7. A calculating machine comprising an accumulator, ordinal actuating means including reciprocable racks for the accumulator, keys for setting up digit values, ordinal racks movable under the control of said keys to corresponding digital settings, means for coupling the ordinal actuating racks with corresponding ordinal key controlled racks when these are in any key set position and for subsequently decoupling said racks from each other, and transmission means operable in one direction to return the key controlled racks to normal position before decoupling with resulting operation of the accumulator and operable in the other direction after decoupling to restore the actuator racks.

8. A calculating machine comprising an accumulator, actuating means including a group of ordinally disposed reciprocatory racks for the accumulator, drive transmitting means including a corresponding group of ordinally disposed members of variable stroke cooperating with said racks and a constant stroke member, digit setting means for determining the strokes of said first mentioned members according to digit values, and pairs of stops on said racks one stop of each pair being movable relatively to its cooperating drive transmitting member to couple the latter to the rack after said member has its stroke determined by the setting means and the other stop of each pair cooperating with the constant stroke member in its movement in one direction to restore the rack after an operation, the movement of the constant stroke member in the opposite direction being transmitted through the coupled variable stroke members and racks to the accumulators.

9. A calculating machine comprising an accumulator, ordinal actuating means including reciprocable racks for the accumulator, keys for setting up digit values, ordinal racks movable AUGUST KO'I'IMANN. 

